Back-off machine



AU@ 26 1947 `R. l. KUFFLER f I 2,426,458y

BACK-OFF MACHINE Filed Aug. so, 1944 9 sheets-sheet 1 Aug. 26, l'19474. R. r. KUFFLER BACK-OFF MACHINE Filed Aug. 30, 1944 9 Sheets-Sheet 2 I Il l.

' ipa-WX Aug. 26, 1947. n.1. KUFFLER 2,426,458

` BACK-OFF MACHINE v Filed Aug. 30,v 1944 9 Sheets-Sheet 3 INVENTOR.

Aug. 26,1947. R. 1. KUFFLER BACK-OFF MACHINE Filed Aug. 30, 1944 9 sheets-sheet 4 INVENTOR 1320/5/70/ j. lf2/Wer Aug. 26, 1947. R. l. KUFFLER 2,426,458

. BACK-OFF MACHINE Filed Aug. so, 1944 sa sheets-sheet 5 Aug. 2'6, 1947.

R. l. KUFFLER BACK-OFF MACHINE.

9 Sheets-Sheet 7 Filed Aug. 30, 1944 Aug. 26, 1947. R. l. KUFFLER 1 2,426,458

' BACK-OFF MACHINE Filled Aug. 30, 1944 9 Sheets-Sheet 8 Aug. 26, 1947. R. l. kUFFLER 2,426,458

BACK-OFF MACHINE Filed Aug. 30, 1944 9 Sheets-Sheet 9 l N VEN TOR.

Patented Aug. 26, 1947 UNITED STATES PATENT OFFICE BACK-OFF MACHINE Roland I. Kufller, Detroit, Mich., assignor of onehalf to Samuel M. Renfrew, Hazel Park, Mich.

Application August 30, 1944, Serial No. 551,915

Claims.

This invention relates to improvements in back-01T machines, and refers to such a machine which may be utilized for work wherein the utes between the teeth are either straight or helical.

Another object of the invention is to provide a back-oilE machine wherein the main spindle is intermittently rotated and the cross slide is reciprocated, and the two movements are so synchronized that the main spindle is turned as the cross slide is moved toward the spindle axis and remains stationary during the return stroke of the cross slide.

Another object of the invention is to provide a back-off machine wherein a Geneva plate is utilized for imparting intermittent rotation to the main spindle and a Whitworth movement is employed for reciprocating the cross slide through an eccentric at a periodically varied speed, so that combination of these movements results in substantially the correct theoretical form being Yimparted to the backed-off surface.

A further object of the invention is to provide a back-oli machine wherein the means for imparting intermittent rotation to the main spindle isso constructed and arranged that the speed of rotation increases during the rst half of each intermittent movement'and decreases during the second half of the movement, thereby minimizing the strains to which the machine is subjected, and virtually eliminating the sudden and violent shocks to which other machines for this purpose are usually subjected.

Another object of the invention is to provide aY for augmenting this rotary distance proportionf Y ately to the longitudinal feed of the saddle on which the cross slide and tool are supported.

A further object of the invention is to provide aback-oli machine including a differential drive in the means for rotating the main spindle intermittently, and a second differential drive in the means for reciprocating the cross slide, and separate manually operable means for adjusting the rotary position of the spindle and for ad- 2 justingthe position of the cross slide along its stroke.

Another object of the invention is to provide such a back-off' machine including indicating means to facilitate the rotary setting of the main spindle 'relative t'o the position of the cross slide along its stroke, yso that'the crossl slide may be accurately set at its position nearest the spindle axis when the spindle and the work carried thereby are so turned that the tool on the cross slide is opposite the beginning of a flute in the Work.

Yet another object of the invention is to provide aN 'back-oir machine including selective meansY for imparting constant rotation to the main spindle whereby reciprocation of the cross slidev is eliminated, so that the machine may be employed for' ordinary lathe work when itis not Yrequired for its primary purpose.

l plate and theV periodically varied drive for the forh'olding "a roller onfthe cross slide in engagementrwith an eccentric member by which the slide is reciprocated.

Figure 10y is a front view of the Geneva plate and someofthe associated parts, and

Figure l1 isa section onthe line Il ll of Figure 10.

Figure` 12 i's aside view showing the means by which rotation at periodically varied speed is imparted to the eccentric member.

Figure 13 is a front view of Figure 12, and Figure 14 is a section on the line I4-IA of Figure 13.

Figure 15 is an end view of the eccentric arrangement fo-r actuating the cross slide, and

Figure 16 is a section on the line I6-|6 of Figure 15.

Figure 17 is another clutch detail.

Figure 18 is a plan view showing the differential adjustment for the main spindle, andY Figure 19 is a front view of Figure 18.

Figure 2O is a plan View showing declutching means for the continuous drive for the main spindie when the intermittent drive is employed, and

Figure 21 is an end view of Figure 20.

Referring t the drawings, I designates a frame of a machine having a main spindle 22 suitably mounted thereon for rotation. While during performance of the backing-off operation this spindle is intermittently turned it is also desirable at times to rotate it constantly at a uniform speed, and therefore selective means are provided whereby intermittent or constant rotation may be imparted to the said spindle 22 through a gear box I0. In the present instance a motor 2 is provided having a pulley 3 thereon which, through a belt 4a, turns a pulley 4 on a shaft 5 extending through one side of the gear box I0. Suitable gearing and associated shifter means are provided in this Vgear box for selectively rotating either of the shafts I4 or 24 `through manipulation of a shifter handle I2. One preferred arrangement of this gearing is indicated in Figures 4, 8, and 20, wherein a gear 6 fixed on the shaft 5 drives a gear 8 on a shaft 9 through an intermediate gear 1. Axially movable on the shaft 9 through the shifter handle I2 is a gear II which 'may be moved either into mesh with a gear I3 fixed on a shaft I4 or into mesh with a gear 23 xed on a shaft 26. When constant rotation of the main spindle 22 is required the gear II is movedV into mesh with the gear I3 on the shaft I4 on which a pulley I5 is secured which turns a pulley I1A on a shaft I8 through belts I6, and a gear I9 slidable on the shaft I8 drives a gear 2| fixed on a sleeve |19 mounted on the main spindle through an intermediate gear 20. A clutch mechanism is providedV for sliding the gear I9 into and out of mesh with the gear 20 so that when the spindle is intermittently turned only the gears 20 and 2| are also rotated. A clutch |12 axially movable on the main spindle 22 is provided for engaging the sleeve |10 so that rotation of the gear V2| may be directly imparted to the said spindle.

To obtain intermittent rotation of the main spindle 22 the gear II is brought into mesh with the gear k23 thereby turning the shaft 24 on which another gear 25 is secured which engages a gear 26 fixed on the shaft 21. Secured also on the shaft 21 is a bellcrank 28 having a pin 29 projecting laterally therefrom. Fixed on a shaft 3|) for rotation therewith is an internal Geneva plate 3| having radial slots 32 formed therein which are disposed at right angles to one another and into each of which in turn the pin 29 projects. The adjacent sides of each succeeding `pair vof slo-ts 32 are curved from one to the other at their inner extremities as shown at 32a, and the axis of each curve 32a. coincides with the axis of the shaft 21 when the latter is so positioned that the pin 29 is travelling from or into one'of the slots 32 in which that curve terminates. Formed integral with the Geneva plate 3| are a plurality of shoes 3Ia the inner face of each of which is curved about an axis which coincides with the axis of the bellcrank 28 when the latter axis is positioned between the axis of the Geneva plate 3| and the center of that shoe 3Ia.

During 9i) degrees of movement of the bellcrank 23, that is during movement of the pin 29 from one Geneva slot V32 to the next around a connecting curve 32a, the Geneva plate 3| rei mains stationary, during the next 135 degrees of movement of the bellorank 28 the pin 29 turns the plate 3E through L15 degrees at an accelerating speed, and during the next 135 degrees of movement of the said crank the pin 29 turns the Geneva plate through 45 degrees at a decelerating speed. Thus during each complete revolution of the bellcrank 28 -the Geneva plate 3| is turned through degrees at the completion of which movement the said plate remains still momentarily. Each shoe Sla in turn receives the heel 28a of the bellcrank by which the Geneva plate is positively held against accidental rotation duringr the 9G degree movement of the bellcrank when the pin 29 is being moved from one slot 32 4to the next.

On they shaft 39 is a gear 34 which through train gears 35, 36, 31, 38 and 39 rotates a shaft 69 having a differential adjustment unit including a housing 4| freely mounted thereon. The gears 36, 35, 3B, and 31 are mounted upon their shafts for ready removal since the rotary distance the main spindle 22 travels between stops depends in part'upon these gear ratios and it is therefore desirable to change them from time to time to suit different work. Mounted in the housing 4I are Vfour meshing bevel gears 62, 63, 46 and 45. The gears 62 and lil are xed on shafts 69 and 66 Vrespectively supported in axial alignment by the housing 6|. Freely mounted on the shaft 65 is a worm wheel 61 which is fixed to the housing 6| to rotate therewith. Rotatably supported on the'. machine is an adjusting shaft 63 having a worm 39 thereon meshing with the worm wheel 41 and a handwheel 5i), so that by turning the latter the worm wheel t1 and the housing II are rotated about the shaft 46 and the shaft 46 is turned. Fixed on the shaft 66 is a gear 5| which meshes with the gear 2| on the sleeve |16 which is freely'rotatable on the main spindle 22. On the latter there is also-a second freely rotatable sleeve I1| between which and the sleeve l |16 an axially movable clutch |12 is provided to engage either sleeve and cause rotation of the said spindle. Thus by moving the clutch |12 into engagementV with the sleeve |19 rotation of the latter drives the main spindle 22. On a countershaft I66 are back gears |61, |69 and |69. The gears |61 and |63 are connected to one another and mounted on splines on the shaft |66 so that the gear |61 may be movedinto mesh with a gear |13 or the gear Y|69 may be moved into meshV witha gearV |16, both the gears |13 and |14 Vbeing xedon the sleeve. |16. The gear I69fixed on the shaft |66 is in constant mesh withV a gear |04 on the sleeve I1I, so that when either gear |61 or |68 is driven the gear |69 may impart rotation to the main spindle 22 by moving the clutch |12. into engagement with the sleeve. I'II. By the inclusion of this back gear arrangement the possible number of stops made during 'each revolution of the main spindle 22 may Ibe greatly increased.. Any conventional worksupporting means such as-a faceplate 52 may be provided on the main spindle 22 for supporting 5 work-AH for' rotation therewith, and the opposite extremity ofthe work? mayv be carried by a conventional' tailstocli.v 52a.

One of the purposes ofi-the differential adjustment above described isvto per-mitvrotary setting ofthe work A so that flutes thereon may be so positioned that a cutting tool B-Ywill have completed one tooth` each time rotation of the main spindle ceases; Anotherl purpose ofthis differential adjustment is tov-provide means'for automatically advancing the-rotary position ofthe work A when the flutes thereinv are-helical-as shown in Figure 2 proportionately to the longitudinal `movement of thev tool along-the worlc and the helix angle of the-flutes. The way in which this latter purpose isachieved -is described hereinafter;

The gear 2| on the main spindle 22a1so meshes with a gear |05fl'xed on a'shaftrl06 which extends into a variable speed gear box- |01 having-suitablegearing thereinsuch asthe gears |20, |2| and |22 shown inFigure 4-1to -drive av shaft |09, and agear |23 also on the shaft |06 which through intermediate gears- |24v and v|25 drives a gear |26 fixed on a feedy screw l-00.- It willi however be understoodv th-at the simplified gearing arrangement just described is-merely illustrative as obviously aconventional change gear arrangementmust also beincludedto Yprovide for-variation in the speed-of rotation of the feed' screw, and thelatterin turn*V may impart longitudinal movement to a saddle 62`fby engagement of -a-releasable split nut |a thereon with the said feed screw. As alreadyfstatedY rotation of the main spindle 22also turns the shaft |09. The latter terminates-at one extremity inf another variable speed gear box l |0 from Awhich a shaft llllsplined forv the major portion of its lengthextends,

though for the sake of simplicity in the drawings the splined shaft ||4- is` merely shown as being driven by agear |2'l Vin'- the boxV ||`0. Freely rotatable on the splined'shaft l l4- is-a gear |f| and mounted on the said? shaft-for axial movement is a sliding clutch |'l5 to engage the gear lill. Meshing both with the gear and with a gear |l3 fixed on a sleeve l-'l'l-freely rotatable on the feed screw |00-is an intermediate gear l`l2; and

axially movable .on the vfeed screw' |00 to engage thegear ||3"is another sliding clutch |-|6g- The clutches ||5=and ||6areconnected to a -ocmmon rotary operating rod |30fso that when the clutch |I5 engages its gearfl theclutch ||6 is released from its gearlil 3;v andy in central orrneutralv position of `therod |30 both gears |A and l I3 are disengaged from their respective clutches, When the clutch |l6--is disengagedv from the gear ||3 andthe clutch l5" is -inY engagement with the gear l'll rotation ofthe shaft lldthrough the gears ||2sand ||3 turns the sleeve and a bevel" gear |03 upon vthe latter turnsa gear |02 on a cross shaft 99. The latter kextends into a gear-box l0| into which the shaft '48 alsovextends, wh'ererotation of the shaft 99 turnsl the shaft 48-or vice versa. WhenV thefeed screw |00v is being employed to advance thesaddle 62 the clutch ll-slidable on the` feedscrew engages the gear ||3-on the sleeve ll'l'and -drives theV latter, the bevel gears Ill?) and |02, the shaft 99 and thus the shaft'll through the gearbox I0'l. If the slplined shaft ||4 is being utilized `for moving vthe saddle longitudinally then the sleeve vl and clutchy ll6 isdisengaged".

Thesplined shaft .H4 .may also be utilized for moving the saddle 62 longitudinally. Axially movable onl theV splined shaft l|4 isa bevel gear |53 which isl retainedin mesh with a gearv |54 on a shaft |5'4a carried by the saddle 62. This shaft l54a through suitable gearing |55 drives a shaft |52 having a pinion |5| freely mounted for rotation thereonwhichy meshes with a racl `|50 carriedV by theV frame l. Also mounted on the shaft |52for axial' movement is a clutch |80 operated into and out of engagement with the pinion |5l by movement of the split nut |00a out vrof and into engagement with the feedscrew. |00'. By rotation of ai threaded member |8| the split nut is tightenedl around the feed screw |00 and by this movement of the nut the clutch |80 is disengaged from the'pinion |5l. Thus an exact feed in a longitudinal direction maybe imparted tothe saddle through the feed screw |00-or the saddle may also beisimilarly moved by rotation of the splined shaft ll4. AgainWhen the splined shaft lll'is not otherwise being turned it may be rotated by a handweel |56 fixed on a spindle |56a mounted onthe frame and having a gear l5'| thereon which meshes witha gear |58 on the said-splined shaft to. move the saddle-longitudinally.

On the shaft-21` isagear 53 which through an intermediate gear 5`41drives a gear 55 fixed on a shaft 55a. Extending from one side' ofthe gear 55i's an eccentric d'rive pin 56`which extends into a transverse slot 5T' formed in a plate 58 mounted on a shaft 59 wh-ich is supported in parallelism with but eccentric to the shaft 55a. As the gear 55 is rotated, due to its axis being out'of alignment with the axis of the shaft 59y and the fact that the distance between the axis of the gear 55 and the center-of the 4pin 56is greater than the distance between' the axesof thev two shafts- 59 and 55a, the speedk of rotation ofthe shaft-59 alternately increases and decreases duringeach v revolution. The distance between the axes of the gear 55 and the pin 56 is \/2 times greater than the distance between the two shafts 59 and 55a. Then the shaft 59'turns through 180 degrees while'thershaft 55 turns through 270 degrees; moreover these rotary movements occur while the Geneva wheel 3|'turns throughv 90 degrees. During the other degree movement ofthe shaft 59` the shaft 550iturns through 90 degrees to complete one revolution, and'during thisperiod the Geneva wheel 3| is at a standstill.

Freely mounted partly on theA shaft 59` and partly on the shaft 65 is a differential adjustment unit including a housing 64; Mounted for rotation on opposed pins 66a and 61a carried'by the said housing are `bevel. gears 66 and 6l respectively each of which mesheswith gears 68 and 69 fixed on the shafts 59 and 65 respectively which are in axial alignment. A wormwheel l0 is secured to the housing 64jfor rotation therewith; and meshing with the worm wheel 'l0 is a worm 'll fixed on a shaft 'l2 operated through a handwheel 13. Toward its opposite extremity and for the major portion of its length the shaft'65 is splined and axially movable thereon is a bevel gear 14 which meshes withV a gear 'l5 ona vertical shaft '|6 vsupported for rotation in the saddle 62 which is` mounted'for longitudinal movement.

This differential is employed in a manner hereinafter described'for setting the movement of a cross slide 96 on the'said saddle to synchronize with the rotary position of teeth of' the work A, as the cross slide andthe tool 'B 'carried thereby mustV be nearest theaxis' ofi` the work' ALI when cutting on each tooth of the latter has just been completed and the tool is opposite the beginning of a flute. v".ihen due to thetiming of the main spindle 22 relativeto the'shaft 59,7the former ceases to turn and the latter turns at a higher speed and brings the cross slide 96 back toi-its position farthest from the work axis to be in position to lcommence the next cut, that is to commence cutting on the next tooth-ofthe work, when the main spindle is again rotated.

Supported vertically in the saddle 62 is a bushing |33 in which a sleeve |34 is mounted for rotation. This sleeve which is keyed to the shaft l@ is provided with an external flange |35 at its upper extremity which is rotatable on the top of the bushing |33. Formed on the upper face of the sleeve |34 are radial serrations |30 which engage corresponding serrations Blb formed on the lower face of an outer eccentric member 6|. The shaft 16 terminates at its upper extremity beneath the top ofthe sleeve |34 in an upward projection |31 of reduced diameter, which extends through an inner eccentric element 6 la on which the outer eccentric member 9| is mounted, and is threaded at its upper extremity to receive a nut |38. Formed on the upper extremity of the eccentric element Bla is an external flange |39 which projects over the top of the outer eccentric member 6| to hold the latter and the innereccentric element Bla as a unit upon the shaft 19, to which the said element is keyed, for rotation with the said shaft after the eiccentricity of the outer member 6| has been set to provide the required length of stroke for a cross slide 90 in a manner hereinafter described.

Mounted for transverse movement on the saddle 62 is a cross slide 96 having pockets |40 therein against the inner ends of which helical springs 91 are retained by plates |4| secured to an indexing ring 62a on the said saddle. These springs V91 tend to move the cross slide and retain a roller 63 rotatably mounted thereon in contact with the eccentric member so that as the latter rotates the slide is reciprocated on the saddle B2 and ring 62a, and the tool B vmounted in a holder |42 upon the said cross slide is moved angularly to the axis of the work A. Through the periodically varied speed of rotation of the shaft 59 the cross slide is moved relatively slowly toward the axis of the main spindle during which time the tool VB is cutting, and is more quickly moved outwardly to bring the tool back into position to start cutting the next tooth of the"`work A. Moreover the intermittent rotary movement of the main spindle 22 is so synchronized with the cross slide movement that during rotation of the spindle the cross slide is moved toward the spindle axis and While the spindle remains stationary the crossslide is moved away :from the said axis.

One of the preferred forms of arrangement for setting the rotary position of the Vwork A relative to the movement of the cross slide 90' is as follows: Mounted on the shaft 21 is a flywheel 11 having an insulating rin'g18 secured to one face thereof. Supported on the inner face of the ring 18 and spaced from the said flywheel is a contact ring 19 having diametrically opposed `outwardly projecting contact pins 80 thereon which project through suitable apertures formed through the insulating ring 18. Supported on the frame is a bracket 8|A which is preferably annular and has diametrically opposed openings formed therethrough in which spring pressed contact points 82 are mounted so that each time; the

8 shaft 21 Vis turned Vthrough 180 degrees the pins 80 each make a contact with one of the points 82. 63 and 84 denote two power leads to a transformer 85 by which rthe incoming current is reduced Ato 6'volts. From the transformer one wire 86 runs to one of the contact points 82 and from the other contact point a wire 81 extends to a contact 88 mounted on an arm 89 insulated from and supported by an indexing ring 62a which is rotatable on the saddle 62 to turn with the cross slide 95 which is mounted for reciprocation on the said ring. In this manner provision is made for turning the slide 95 and the tool B angularly relative to the axis of the work A. The contact 88 is mounted in wiping relation with the contact 90 which is grounded on the machine. From the transformer 85 a second wire 92 extends to a light bulb 93 the other side of which is also grounded on the frame through a lead 94.

When the rotary position of the shaft 21 is such that the contact pins 80 engage the points 82 the handwheel 13 is rotated until the eccentric member 6| is so positioned that a connection is made between the contacts 08 and 90 then the circuit is completed and the light bulb 93 is illuminated. The contact 90 is so positioned that it makes a connection with the contact 88 when the eccentric member 6| is so turned that the cross slide is at its most forward position and nearest the axis of the work A. The tool B must reach that position immediately prior to the time the Geneva plate 3| ceases to turn and causes stoppage of the main spindle 22; then the tool B and the cross slide 9B are moved outwardly from the spindle axis to the position to commence cutting the next tooth on the work prior to the time that the work A has been rotated sufficiently for the next tooth thereon to be contacted by the said tool.

From the foregoing it will be clearly seen that the number of stopsA made during eachrevolution of the main'spindle may be Varied over a wide range. The'distance-which the main spindle rotates during each movement may be increased or decreased by rotation of. the worm wheel 41 either manually or through the gear box |0|. The distance through whichthe cross slide is reciprocated may be varied by adjustment of the outer eccentric member upon the inner eccentric element, The speed of longitudinal movement of the saddle relative to the speed of rotation of the main spindle is controlled through gearing in the box |01 when the feed screw |00 is in engagement with the saddle and through the gears in the box ||0 when the splined shaft is employed for moving Vthe saddle. The feed screw provides accuratemovement of the saddle relative to the spindle rotation and the splined shaft provides approximately accurate movement thereof which is sufficiently clo-se for longitudinal feeding of the tool. VThrough rotation of the shaft 12 theV stroke of the cross slide 96 may be readily set to synchronize with the-intermittent operation of the spindle 22 and the position of flutes on work A rotatedrwith the said spindle. Again simple and easy means are provided for setting the rotary positionY of the eccentric member 6| so that its movement is :correctly timed relative to the intermittent rotation of the main spindle22.

' During thel operation of the ,machine the main spindle 22. is rotated intermittently in one direction whilethe tool travels'from one end of the workpiece toY the other.V When the workpiece has teeth or work faces which are continuous throughout its whole length as shown in both Figures 2 and 3, and in most other cases, the tool merely takes a narrow and longitudinally overlapping cut on each tooth or work face each time the latter passes, as is usual in vlathe operations. If the flutes in the workpiece are straight as shown in Figure 3 the shaft 48 remains idle and the intermittent spindle movement is so set that during each movement it turns through 360 divided by the number of flutes in the workpiece. If the flutes are helical the 'setting of the main spindle movement is the same except that the shaft 48 is also turned-either bythe Vfeed screw or the splined shaft H4 whichever is being employed for moving .the saddle 62-to increase or decrease each angular movement of the spindle so that upon substantial completion of each revolution it has turned through 360 plus orrminus (according to the direction in which the flutes are wound) the angular distance between two points on one tooth or work face initially contacted on two consecutive cuts. This angular distance depends on two things: The coarseness of the longitudinal feed of thesaddle and tool, and the helix angle of the iiutes. The adjustment for pitch or coarseness of the feed is automatically taken care of since the shaft 48 is turned either by the feed screw .or the splined shaft; and the gear combination Vin the box llliis .selected according to the helix angle of the flutes. Itwill also be noted that adjustment of the length of the stroke of the cross slide is made by relative rotation of the circular eccentric member 6l and the eccentric element Gla, and due tothe -circular shape of the member the back-off form produced is correct irrespective of the length of the stroke.

While in the foregoing the preferred embodiment of the invention has been described vand shown it is understood that alterations andimodications may be made thereto provided they fall within rthe lscope of the vappended claims; and

. again a detailed showing has not been made -of the conventional change speed gearing arrangements employed since Vtheir use is old and their inclusion would merely complicate the drawings.

I claim:

1. A back-off .machine including a continuous drive, a main spindle, means including a Geneva plate intermittently turned by the continuous drive for imparting intermittent rotation to the main spindle,.a cross slide mounted formovement angularly to the axis ofthe main spindle, means actuated bythe continuous drive for reciprocating the cross slide,-and said lmeans for reciprocating the cross slide and the means for imparting intermittent rotation to the main -spindle being Y soY synchronizedvthat the cross slide is moved toward Ythe mainspindle axis during rotation of the spindle and away Yfrom said Aaxis when the spindle `'is stationary,

"2. A 'back-off machine including a continuous drive,` a Vmain spindle, a Geneva plate, 4means actuated "by t-he continuous drive for'intermittently'rotating the Geneva plate, means'for turning the main spindle when the Genevaplate is turned, means interposed -betweenjthe Geneva plate -and the main spindle for changing the angulardistance through Vwhich said spindle is turned'- during each movement of the Geneva plate, across s'lide `mounted for movement angularly -to the axis of the main spindle, means actuated by the continuous drive for reciprocating the cross-slide, and 'said means for intermittently rotating -the Geneva plate and the means for reciprocating the cross slide being synchronized so that the cross slide is moved toward the main spindle axis vduring rotation of the spindle and away from said axis when the spindle is sta tionary.

35A back-off machine including the combination Vset forth in `claim 2, including a diierential unit interposed between the Geneva plate and the'main spindle, and manually operable means connected to said `unit for turning the main l latter, and the means for intermittently turning the main spindle and the means for reciprocating the cross slide being 'synchronizedsothat the cross slide is moved toward .thespindleaxis when the spindle isturning and away from said axis when the spindle is stationary.

5. `A back-off machine including a continuous drive,'a main spindle, means including a Geneva plate intermittentlyturned by the continuous drive Afor intermittently turning the'main spindle, a cross slide mounted for .reciprocationangularly tothe raxis of the .main spindle, meansV actuated by the continuous drive for reciprocating the cross slide whereby the reciprocation vsynchronizes with the Yintermittent rotation of the main spindle, said last named means 'including adifferential drive, and, manually operable means..for turning the differential drive to'initially position the reciprocating movement of'the cross slide relative to the intermittent rotation of the main spindle.

6. A back-offv maschine including a continuous drive, amain spindle, means operated -by the continuous drive for turning the mainspindleintermittently, a cross slide mounted for reciprocation angularly to the axis of the main spindle, means actuated by the continuous drive for reciprocating the cross slide'at aperiodically varied speed, the last knamed means including two rotarily adjustable circular eccentrically mounted members arranged one within the other for actuating the crossslide whereby the length of stroke of the icross slide may be kvaried by relative rotary adjustment of the said members, and the vmeans for intermittently turning the main spindle and the means for reciprocating the cross slide being synchronized so thatthe cross slide is moved toward the spindle axis when the spindle is turning and away from said axis when the spindle is stationary.

17. A back-off .machine including a continuous drive,l a main spindle, means including a'Geneva plate intermittently turned by `the continuous driveor intermittently turning said spindle, rselective means interposed .between thefGeneva plate and the main s-pindle for changing the rotary distance through which the spindle is turned (during each movement, a. cross slide mounted for movement angularly toy the axis `of the main spindle, means operated by the continuous drive including an inner eccentric element and an outer eccentric member rotarily adjustable thereon for reciprocating the cross slide whereby the rlength of stroke of the latter 'may be adjusted, 'and the .means for intermittently turning the main spindle and the Vmeans for reciprocating the cross slide being synchronized so that the cross slide is moved toward the spindle axis when the spindle is turning and away from said axis when the spindle is stationary.

8. A back-off machine including a continuous drive, a main spindle, means including a Geneva plate intermittently turned by the continuous drive for intermittently turning said spindle, a saddle mounted for longitudinal movement, a feed screw, means for turning the feed screw by rotation of the main spindle, releasable means on the saddle for engaging the feed screw whereby the saddle may be moved during rotation of the main spindle, a cross slide mounted for reciprocation on the saddle, means actuated by the continuous drive for reciprocating the cross slide, and the means for intermittently turning the main spindle and the means for reciprocating the cross slide being synchronized so that the cross slide is moved toward the spindle axis when the spindle is turning and away from the spindle axis when said spindle is stationary.

9. A back-off machine including a continuous drive, a main spindle, means including a Geneva plate intermittently turned by the continuous drive for intermittently turning said spindle, a saddle mounted for longitudinal movement, releasable means driven by rotation of the main spindle for moving the saddle, a cross slide mounted for reciprocation on the saddle, means actuated by the continuous drive for reciprocating the cross slide, and means actuated through the means for moving the saddle for increasing or decreasing the rotary distance through which the main spindle is turned during each movement.

10. A back-off machine including a continuous drive, a Geneva plate, means operated by the continuous drive for intermittently turning the Geneva plate, a main spindle, means rotated by the Geneva plate including a differential drive for turning the main spindle, means operated by rotation of the main spindle and through the differential drive for augmenting the rotary distance the main spindle is turned during each movement, a saddle, a cross slide thereon, means actuated by the continuous drive for reciprocating the cross slide whereby the movement of the latter is synchronized with the intermittent rotation of the spindle, means operated by the spindle rotation for moving the saddle, and the means for augmenting the rotary distance the main spindle is turned being operated by and proportionately to the saddle movement,

11. A back-off machine including a :continuous drive, a shaft rotated thereby, a pin eccentrically mounted on the shaft, a Geneva plate mounted for rotation and having radial slots therein connected to one another at their inner extremities, said pin projecting into each slot in turn to impart intermittent rotation to said plate, a main spindle, means driven by the Geneva plate for turning said spindle including means for adjusting the angular distance through which said spindle is moved during each intermittent movement, a cross slide, and means actuated by the continuous drive for reciprocating the Icross slide whereby movement of the latter is synchronized with the intermittent movement of the spindle.

12. In a back-off machine, the combination of a continuous drive, a main spindle, means operated by the continuous drive for imparting intermittent rotation to the main spindle, a shaft turned by the continuous drive, an eccentric drive pin carried by said shaft, a second shaft parallel but out of alignment with the rst shaft, a plate on said second shaft having a transverse slot in one face into which said drive pin extends whereby rotation of the first shaft turns the second shaft at a periodically varying speed, a cross slide, and means driven by said second shaft for imparting reciprocation to the cross slide.

13. The combination set forth in claim 1, including a differential drive interposed between the Geneva plate and the main spindle for driving the latter, a shaft for turning the differential drive whereby the angular distance through which the main spindle is turned during each rotary movement is either increased or decreased according to the direction of rotation of said shaft, and means for turning the shaft.

14. The combination set forth in claim 1, including a drive mechanism operated by the icontinuous drive for` intermittently turning the Geneva plate, a rotary element engageable with the main spindle for turning the latter, another drive mechanism operable by the continuous drive for continuously turning the rotary element, a clutch for selectively engaging either of said drive mechanisms with the continuous drive, and means for engaging or disengaging the rotary element with the main spindle.

15. A back-off machine including a continuous drive, a main spindle, means including a Geneva plate intermittently rotated by the continuous drive for intermittently turning the spindle, a saddle mounted for longitudinal movement, a shaft, means for turning the latter by rotation of the main spindle, a cross slide mounted for reciprocation on the saddle, means actuated by the continuous drive for reciprocating the cross slide at a periodically varied speed, the means for intermittently turning said spindle and the means for reciprocating the cross slide being so synchronized that the latter is moved toward the spindle axis when the spindle is turning and away from said axis when the spindle is stationary and releasable coacting means on the shaft and saddle for moving the latter during rotation of the main spindle whereby the cross slide may be moved longitudinally with the saddle during movement of the said slide relative to the axis of the said spindle, and means for engaging and releasing said coacting means.

16. A back-off machine including a lcontinuous drive, a main spindle, means operated by the continuous drive for intermittently turning the spindle, a saddle mounted for longitudinal movement, releasab-le means driven by rotation of the main spindle for moving the saddle, a cross slide mounted for reciprocation on the saddle, an'd means including a Whitworth drive actuated by the continuous drive for reciprocating the cross slide at a periodically varied speed, the means for intermittently turning the main spindle and the means for reciprocating the cross slide being so synchronized that the cross slide is moved toward the spindle axis when the spindle is turning and away from said axis when said spindle is stationary.

17. A back-off machine including a continuous drive, a main spindle, means driven by the continuous drive for intermittently turning said spindle, a saddle mounted for longitudinal movement, releasable means driven by rotation of the main spindle for moving the saddle, a cross slide mounted for reciprocation on the saddle, means including a Whitworth drive actuated by the continuous drive for reciprocating the cross slide at a periodically varied speed. and means actuated 13 by the means for moving the saddle for increasing or decreasing the rotary distance through which the main spindle is turned during each movement.

18. A back-01T machine including a continuous drive, a main spindle, means on the spindle for rotating work having teeth thereon, means driven by the continuous drive for intermittently turning said spindle and work, a cross slide mounted for reciprocation angularly to the spindle axis, a tool on the cross slide, means including a Whitworth drive actuated by the continuous drive for reciprocating the cross slide at periodically varied speed, and the last named means also including a rotarily adjustable eccentrically mounted circular member for moving the cross slide whereby the length of the stroke of the latter may be adjusted to cut the back-ofi on teeth of various depths.

19. A back-off machine including a continuous drive, a main spindle, means on the main spindle for rotating a workpiece having teeth thereon, means including a Geneva plate turned by the continuous drive for intermittently rotating the spindle and workpiece, a cross slide mounted for reciprocation angularly to the spindle axis, means including a Whitworth drive actuated by the continuous drive for reciprocating the cross slide at periodically varied speed, the last named means including a rotarily adjustable circular member eccentrically mounted for moving the cross slide whereby the length of the reciprocating stroke is adjustable to suit the depth of the teeth on the workpiece, and the Geneva plate and the Whitworth drive being so synchronized that a proper back-off form is maintained at all rotary adjustments of the circular member.

20. In a machine, the combination of a continuous drive, a main spindle, a Geneva drive interposed between the continuous drive and the main spindle whereby intermittent rotation is imparted to the latter, a cross slide, means for reciprocating the cross slide angularly to the axis of the main spindle, a drive means including a Whitworth movement driven by the continuous drive for actuating the reciprocating means at periodically varied speed, and a differential adjustment interposed between the Whitworth movement and the reciprocating means by which the cross slide movement may be set in relation to the intermittent rotation of the main spindle so that the latter ceases to turn just after the cross slide reaches its inward limit of travel.

21. The combination in claim 20, including indicating means connected to the Geneva drive and to the reciprocating means for checking the synchronization of the spindle and cross slide movements.

22. The combination in claim 20, including electrical indicating means connected both to the Geneva drive and to the reciprocating means by which a signal is given when the spindle and cross slide movements are synchronized.

23. In a machine, the combination of a continuous drive, a main spindle, a Geneva drive interposed between the continuous drive and the main spindle whereby intermittent rotation is imparted to the latter, a cross slide, means for reciprocating the cross slide angularly to the axis of the main spindle, a drive means including a Whitworth movement driven by the continuous drive for actuating the reciprocating means at periodically varied speed, and a differential adjustment interposed between the Geneva drive and the main spindle by which the intermittent rotation of the main spindle may be set in relation to the reciprocation of the cross slide so that each time the spindle ceases to turn work rotated therewith is angularly correctly positioned relative to the cross slide.

24. The combination in claim 23, including indicating means connected to the Geneva drive and to the reciprocating means for synchronizing the angular position of the work at the conclusion of each rotary movement of the spindle relative to the position of the cross slide along its path of travel.

25. 'Ihe combination in claim 23, including electrical indicating means connected to the Geneva drive and to the means for reciprocating the cross slide by which a signal is given when the angular position of the main spindle is synchronized with the position of the cross slide along its path of travel.

ROLAND' I. KUFFLER.

REFERENCES CITED The following references are of record in the file of this patent:

UNITED STATES PATENTS Number Name Date 1,917,905 Schellenbach July 11, 1933 1,985,477 i Wolf Dec. 25, 1934 2,124,213 Shackleton July 19, 1938 1,320,468 Hampe Nov. 4, 1919 1,396,292 Shields Nov. 8, 1921 1,429,617 Muller Sept. 19, 1922 1,700,327 Mueller Jan. 29, 1929 1,731,481 Edgar Oct. 15, 1929 1,744,783 Mayo Jan. 28, 1930 1,809,377 Edgar June 9, 1931 2,360,576 Overstedt Oct. 17, 1944 

